Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D25/00—Fluid-actuated clutches
  • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D25/00—Fluid-actuated clutches
  • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
  • F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
  • F16D25/083—Actuators therefor
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D25/00—Fluid-actuated clutches
  • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches

Definitions

• the invention relates to a disengaging device.
• the invention relates to a disengagement device for the axial actuation of a friction clutch.
• a friction clutch for example a multi-plate clutch running in an oil bath
• a friction clutch which comprises a number of steel and friction disks, one type of disks being connected in a torque-locking manner to an output shaft of the drive motor or a drive shaft of the manual transmission.
• the lamellae are arranged alternately in the axial direction and are pressed against one another by means of spring force, so that a frictional connection is produced which connects the output shaft of the drive motor to the drive shaft of the gearbox in a torque-locking manner.
• a release bearing is actuated counter to the direction of force of the spring, so that the frictional engagement between the disks canceled and the torque between the output shaft and the drive shaft is interrupted.
• a hydraulic actuator is used, which is arranged annularly around the output shaft of the drive motor.
• two disc clutches are accordingly installed, which can be actuated independently by concentrically arranged around the output shaft of the drive motor hydraulic disengaging.
• an axial connection for the hydraulic fluid can be provided in the carrier element.
• the housing forms a carrier housing.
• the carrier element can thus take over the task of supporting the disengagement device on the clutch bell and at the same time that of the guidance of the fluid.
• the disengagement device can thereby be easier and less expensive to produce.
• the attachment of the support member may make a separate mounting component, such as a clamping claw, superfluous.
• the fluid connection between the axial hydraulic port and the corresponding hydraulic port in the clutch bell can be made automatically during assembly of the clutch release on the clutch bell.
• Radial distances of the attachment points to a rotational axis of the friction clutch may be outside a radial contour of the friction clutch. This can be mounted in the clutch bell when the friction clutch is already mounted in the axial direction on the disengaging device. In this way, the disengagement device can be mounted together with the friction clutch as a unit to be handled separately and, if appropriate, integrated with it. Such an arrangement of the disengagement device is also called "cover-tight".
• the disengagement device is further configured to disengage a further friction clutch independently of the other friction clutch, wherein the carrier element comprises a further axial connection for fluid.
• the carrier element has an axial contact surface for engagement with the clutch bell in the region of the axis of rotation and the carrier element is shaped so that the attachment points are axially separated by a predetermined gap from the clutch bell when the contact surface bears against the clutch bell, so that the carrier element can be a-xial biased by approaching the attachment points to the clutch bell to connect the axial ports fluid-tight.
• an axial spring element for connecting the attachment points with the clutch bell is provided.
• the spring element is set up to ensure that a predetermined pretensioning of the carrier element is maintained or not exceeded.
• the carrier element is integrally formed and includes both the terminals and the attachment points or connecting elements to the attachment points.
• the carrier element comprises a hydraulic connecting element for receiving the terminals and a fastened to the connecting element, substantially disc-shaped connecting element for attachment to the clutch bell.
• the disc-shaped connecting element can be inexpensively produced, for example, from a sheet metal.
• the connecting element may be formed from a light metal or steel. Attachment points can be provided both on the connecting element and on the connecting element, so that the connecting element can be made compact and material-saving, while the connecting element can be dimensioned weak, since not all fastening forces of the connecting element are passed through the connecting element. Production costs can thus be reduced.
• the separate connecting member d em space and / or a weight of the disengaging device can be reduced. Furthermore, savings in the production of the release device can be achieved.
• a fitting device is provided to ensure a clear rotational installation position of the support element.
• a misallocation or blockage of one of the hydraulic connections can be counteracted thereby.
• Adjacent angles between attachment points with respect to the axis of rotation may be different.
• a rotational installation position of the carrier element or of the connecting element can likewise be ensured.
• the carrier element comprises a radial contact surface for engagement with the clutch bell in the region of the axis of rotation, in order to ensure a centering of the disengagement device with respect to the clutch bell.
• An installation position of the disengagement device can thereby be largely predefined, so that an installation clearance can be reduced and an incorrect installation position can be prevented.
• Figure 1 is a longitudinal section through a disengaging device
• Figures 2 to 4 details of the disengaging device of Figure 1;
• FIG. 5 perspective views of a support member of a disengaging device according to Figures 1 to 4.
• FIG. 6 shows perspective views of a carrier element of a disengagement device in a further embodiment.
• FIG. 1 shows a longitudinal section through a disengaging device 100.
• the disengaging device 100 is shown in the assembled state in a clutch bell 105.
• Two friction clutches in particular in a oil bath running multi-plate clutches, which can be actuated and disengaged independently by means of the disengagement device 100, close to the left to the disengaging device 100 and are not shown.
• the clutch bell 105 is a kesseiförmige depression on the housing of an engine, in particular an internal combustion engine for driving a motor vehicle.
• the internal combustion engine extends from FIG. 1 to the right.
• An output shaft of the internal combustion engine (not shown) extends from the engine side to the left through the disengagement device 100 to the multi-plate clutches.
• the multi-plate clutches, the output shaft and parts of the disengaging device 100 are rotatably arranged about a rotation axis 110.
• the disengaging device 100 comprises a carrier element 115, which is designed in one piece with the housing of the disengaging device 100, a first hydraulic actuator 120, a second hydraulic actuator 125 and a clutch carrier 130.
• the carrier element 115 is preferably made of a light metal cast part.
• the carrier element 115 comprises a plurality of attachment points 135, one of which is shown in greater detail in region A in FIG. 2, an axial abutment surface 140 and a radial abutment surface 145 in region B, which are shown in greater detail in FIG. 3, and hydraulic connections 150 in region C, which are shown in more detail in Figure 4.
• the attachment points 135 lie with respect to the axis of rotation 110 in distances which exceed a radius of the coupling carrier 130, so that the disengagement device 100 can be mounted on the clutch bell 105, when the clutch carrier 130 is already attached to the carrier element 115.
• the hydraulic actuators 120 and 125 are arranged concentrically about the axis of rotation 110. Each of the hydraulic actuators 120, 125 is adapted to exert a left-acting force against the clutch bell 105 when a hydraulic pressure is built up in a corresponding hydraulic supply line. The force of each hydraulic actuator 120, 125 counteracts a spring force of the associated multi-plate clutch, which loads the respective clutch in the axial direction and thereby produces a frictional connection. Upon actuation of one of the actuators 120, 125, the spring load is released or the slats or friction plates are lifted off from each other in the axial direction, so that the frictional connection is canceled.
• the clutch carrier 130 is adapted to an abutment for one or both of
• tension springs that compress one of the multi-plate clutches in the axial direction may be connected at their right ends to the clutch carrier 130.
• the coupling carrier 130 is rotatably attached to the carrier element 115 by means of a roller bearing 155, preferably a shoulder ball bearing.
• FIG. 2 shows a detail of the disengaging device 100 from FIG. 1 in the area A marked there. The detail illustrated illustrates an attachment of the upper attachment point 135 to the clutch bell 105.
• the attachment point 135 is formed by a contact surface 205 of an extension of the support member 115 and a recess 210 for receiving a through the. Bearing surface 105 extending screw (not shown).
• the contact surface 205 of the support member 115 is adapted to be in abutment with a contact surface 215 of the clutch bell 105.
• the carrier element 115 is shaped so that it already rests against the clutch bell 105 in the axial direction in the region of the axis of rotation 110 before the contact surfaces 205 and 215 are in contact with one another.
• the contact surfaces 205 of the support member 115 and 215 of the clutch bell 105 can be approximated in the axial direction to each other, wherein the support member 115th is placed under an axial bias.
• FIG. 3 shows a further detail of the disengaging device 100 from FIG. 1 in the region B marked there.
• the detail shows abutment surfaces between the carrier element 115 and the clutch bell 105 in the region of the axis of rotation 110.
• the axial abutment surface 140 of the carrier element 115 bears against an axial abutment surface 305 of the clutch bell 105. This system prevents further movement of the support member 115 to the right, whereby the gap 220 in Figure 2 is as long as the support member 115 is tension-free, that is unsupported in the region of the attachment point 135 to the right.
• the radial contact surface 145 of the carrier element 115 is in contact with a radial contact surface 310 of the clutch bell 105.
• the contact surfaces 145 and 310 are rotating around the axis of rotation 110, so that the disengagement device 100 is centered about the rotational axis 110 with respect to the clutch bell 105.
• FIG. 4 shows yet another detail of the disengaging device 100 from FIG. 1 in the region C drawn in there.
• the detail shows a hydraulic connection 150 of the disengaging device 100.
• the hydraulic connection 150 is assigned to one of the hydraulic actuators 120, 125.
• a first channel 405 extends within the support member 115 in a direction parallel to the axis of rotation 110. Not completely visible further channels within the support member 115 connect the first channel 405 with a cylinder 410 of one of the actuators 120, 125.
• Die Zylinder 410 Sind ring- hrs. toroidally formed around the axis of rotation 110.
• hollow-cylindrical pistons 415 are accommodated to the left in the cylinders 410 and close off the cylinders 410 in a fluid-tight manner to the left.
• Axially aligned with the first channel 405 is a second channel 420 which extends within the clutch bell 105. Opposite ends of the channels 405 and 420 are each widened in a cone shape. In an area within the cone-shaped extensions and between opposite ends of the channels 405 and 420, an elastic seal (not shown), for example an O-ring, is optionally provided. This produces a fluid-tight connection between the piston 410 of the respective actuator 120, 125 and the second channel 420 of the clutch bell 105.
• the second channel 420 may in particular be connected to a hydraulic control device which is adapted to select gear stages in a transmission which is connected to the clutches which can be actuated by means of the actuators 120, 125.
• FIG. 5 shows perspective views of the carrier element 15 of the disengaging device 100 according to FIGS. 1 to 4.
• the left-hand illustration shows a surface facing the clutch bell 105
• the right-hand representation shows a side of the carrier element 115 facing away from the clutch bell.
• annular recesses for forming the cylinder 410 and the abutment surfaces 140 and 145 are formed in a hub region about the axis of rotation 110 (not shown) in the support member 115.
• One of the extensions 505 includes the hydraulic ports 150.
• the attachment points 135 are not evenly distributed on a circumference, but instead angles between adjacent attachment points 135 with respect to the axis of rotation 110 are unequal.
• FIG. 6 shows perspective views of the carrier element 115 of the disengaging device 100 in a further embodiment.
• a side facing the clutch bell 105 is shown; in the right-hand region, a side of the carrier element 115 facing away from the clutch bell 105 is shown.
• the carrier element 115 shown in FIG. 6 comprises two elements which are connected to one another.
• the first element is a hydraulic connection element 605, which substantially corresponds to the carrier element 115 of FIG. 5 without the extensions 505.
• a dowel pin 610 and holes 615 are provided for receiving further dowel pins to define a rotationally clear mounting position of the hydraulic connection element 605.
• the carrier element 115 shown in FIG. 6 comprises a connecting element 620, which is connected to the connecting element 605, for example by means of an interference fit.
• the connector 620 is substantially disc-shaped and may include one or more circumferential beads or grooves to enhance axial spring characteristics of the connector 620.
• a section of the connecting element 620 is shown cut off in the left and in the right region.
• the attachment points 135 are in a greater variety than in the embodiment of Figure 5 and may be evenly distributed on a circumference about the axis of rotation 110 (not shown).

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
• Mechanical Operated Clutches (AREA)

Priority Applications (5)

Applications Claiming Priority (2)

Related Child Applications (1)

Publications (1)

Family

ID=47010112

Family Applications (1)

Country Status (6)

Cited By (1)

Families Citing this family (8)

Citations (5)

Family Cites Families (7)

• 2012
  • 2012-06-21 WO PCT/DE2012/000636 patent/WO2013007231A1/de active Application Filing
  • 2012-06-21 DE DE102012210523A patent/DE102012210523A1/de not_active Withdrawn
  • 2012-06-21 CN CN201280034637.1A patent/CN103842679B/zh active Active
  • 2012-06-21 JP JP2014519418A patent/JP6076340B2/ja active Active
  • 2012-06-21 DE DE112012002915.1T patent/DE112012002915A5/de not_active Withdrawn
  • 2012-06-21 EP EP12769878.5A patent/EP2732175B1/de active Active
• 2014
  • 2014-01-02 US US14/146,191 patent/US9200683B2/en active Active

Patent Citations (5)

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